EP0131881B1 - Rotational flexible coupling with torque variations damping - Google Patents

Rotational flexible coupling with torque variations damping Download PDF

Info

Publication number
EP0131881B1
EP0131881B1 EP84107975A EP84107975A EP0131881B1 EP 0131881 B1 EP0131881 B1 EP 0131881B1 EP 84107975 A EP84107975 A EP 84107975A EP 84107975 A EP84107975 A EP 84107975A EP 0131881 B1 EP0131881 B1 EP 0131881B1
Authority
EP
European Patent Office
Prior art keywords
shaft coupling
coupling according
disc
clutch
projections
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired
Application number
EP84107975A
Other languages
German (de)
French (fr)
Other versions
EP0131881A3 (en
EP0131881A2 (en
Inventor
Curt Dipl.-Ing. Krönert
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
KROENERT, CURT, DIPL.-ING.
Original Assignee
Kronert Curt Dipl-Ing
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from DE19833325214 external-priority patent/DE3325214C2/en
Priority claimed from DE19843400127 external-priority patent/DE3400127A1/en
Priority claimed from DE19843408286 external-priority patent/DE3408286A1/en
Application filed by Kronert Curt Dipl-Ing filed Critical Kronert Curt Dipl-Ing
Priority to AT84107975T priority Critical patent/ATE42808T1/en
Publication of EP0131881A2 publication Critical patent/EP0131881A2/en
Publication of EP0131881A3 publication Critical patent/EP0131881A3/en
Application granted granted Critical
Publication of EP0131881B1 publication Critical patent/EP0131881B1/en
Expired legal-status Critical Current

Links

Images

Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16DCOUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D3/00Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/80Yielding couplings, i.e. with means permitting movement between the connected parts during the drive in which a fluid is used
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16FSPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F2230/00Purpose; Design features
    • F16F2230/0052Physically guiding or influencing
    • F16F2230/0064Physically guiding or influencing using a cam

Definitions

  • the invention relates to a torsionally flexible, vibration-damping shaft coupling according to the preamble of claim 1.
  • Such a shaft coupling is known from DE-A-3148338.
  • Couplings are known (for example according to DE-A-24 44 787 and DE-B-30 33 302) in which ° are arranged between a primary and a secondary part radially directed leaf spring assemblies clamped by intermediate pieces, between which there are for the purpose of damping Oil-filled chambers are located, the oil being pressed from one chamber to another when loaded.
  • DE-A-32 28 673 A-1 discloses a torsional vibration damper intended for use in vehicle friction clutches, in which the torque is transmitted from the shaft-shaped primary part to the approximately drum-like secondary part carried by it via an annular coupling body arranged therein, which engages with a thrust device (trapezoidal thread) allowing longitudinal displacements and is slidably connected to the periphery of the secondary part by means of axial toothing, with a plate spring on each side of the coupling body, which is supported on the wall of the secondary part.
  • a thrust device trapezoidal thread
  • coupling members the inclined surfaces of which are tangent to the axis of rotation, as in the case of the aforementioned DE-B-32 28 673 A1, are also subject to a torsional backlash which cannot be eliminated, by which speed shocks are generated when the torque is reversed, which have a very harmful influence on the coupling and exercise the connected machines.
  • a shaft coupling in the manner of a torsional vibration absorption device in which an oil-loaded housing is provided with a multi-plate friction clutch, the plates of which are acted upon by a plate spring pair and axially on the other side abuts a coupling ring which is guided axially in a toothing of the housing and bears on the primary part of the coupling with axially projecting teeth with oblique flanks which engage in corresponding, curved recesses on the end face of the primary part.
  • the coupling ring By rotating the two coupling parts against each other, the coupling ring is therefore moved axially and presses on the multi-plate clutch, which thus acts as an attenuator for torsional vibrations. Since only one pair of disc springs is arranged concentrically to the output shaft in this type of construction, only a relatively small torsional force can be transmitted with such a design if the space requirement of the damping device is not to be too great.
  • the object of the invention is to create a shaft coupling of this type which has a high specific transmission capacity and is therefore space-saving, the transmission mechanism which converts the tangential movement of the primary part into an axial movement and from there again into a tangential movement of the secondary part is as abrasion-free as possible and fully utilizes the entire spring volume regardless of the direction of the torque.
  • the characterizing features of claim 1 are provided in a shaft coupling of the type mentioned.
  • a shaft coupling with a small number of individual parts is achieved, which accommodates packets of spring elements, in particular disk springs, which are guided on the inside on bolts in a space-saving manner.
  • This coupling is also very narrow in that the hub extends completely into the housing.
  • the arrangement of the support disc ensures that all spring assemblies act evenly and the abrasion remains low.
  • the support disk is expediently designed as an axial bearing.
  • a particularly advantageous embodiment of the invention consists in that two clutch disks are arranged between the primary part and the secondary part, which are provided with the projections on the mutually facing sides, packages of disc springs being arranged on both sides of the pair of disks.
  • the wreath-like projections can more after outer diameter or more according to the inner diameter of the clutch discs, depending on whether the design is based on a higher torque to be transmitted and less rotation or a larger rotation at a lower torque.
  • Particularly balanced ratios result if, according to the invention, these are arranged approximately in the middle between the outer and inner diameters of the clutch disks.
  • An advantageous development of the invention provides a device by means of which an optionally finely controllable damping is made possible over the entire torque curve, the damping characteristics being changed either automatically or / and from the outside.
  • a tubular control part provided with a radial seal at the outer end can be provided, which cooperates with corresponding axially directed channels in the primary or secondary part, which channels are provided with a plurality of throttle openings lying one behind the other on axially parallel planes and leading into the coupling interior are which are swept by the radial seal during the working stroke, with at least one throttle opening from the front of the clutch or the like with a regulating screw. its cross section is changeable.
  • an advantageous embodiment consists in that at least one throttle opening can be changed in cross-section from the front side of the coupling with a regulating screw.
  • the regulating screw can also be designed as an automatically operating, pressure-dependent valve, which can be adjusted from the outside.
  • Another favorable embodiment consists in that as a flow opening between the chambers there are bores in the support disk and in the adjacent clutch disk in the region of the bolts on which the spring elements are held, with a control part being arranged in each bore of the support disk.
  • Torsionally flexible couplings the mode of operation of which is based on the fact that a circumferential force is converted into an axial force under load and from there back into a circumferential force
  • the disadvantage provided that the associated axial displacement takes place via coupling connections subject to friction, is that the coefficients of friction can be subject to fluctuations that occur under depend, among other things, on the specific load on the material pairing, the lubricant supply and the speed of the escort. If clutches of the type according to the invention are to respond sensitively even at high frequencies, then under certain conditions sticking back can occur which interferes with the uniform development of the force.
  • Fig. 1 designated (1) the primary part, which is connected to the housing (2), which is closed by the cover (3).
  • the secondary part (5) is held on the cover (3).
  • the secondary part (5) is provided with a flange (5a) for connection to the machine to be driven or also driven.
  • a concentric, ring-like clutch disc (14) is arranged next to the wall of the latter.
  • the clutch disc (14) When a torque is introduced into the primary part (1), the clutch disc (14) is taken along and through the projections (9) also the secondary part (5). At the same time, the projections slide, the side surfaces (9a) (see Fig. 4a to 4d) an inclination of e.g. Have 20 ° to 40 °, in the circumferential direction on each other, the axial component of the sliding force exerting pressure on the clutch disc (14) and via this on the spring element (8) assembled to form a spring assembly, which are designed as disc springs. With increasing torque, this can take place until, depending on the design of the coupling, the projections (9) either slip, i.e.
  • the coupling works as overload protection for the connected machine, or stops are provided for limiting the spring travel, when reached the coupling then acts in a torsionally rigid manner, i.e. the clutch is protected.
  • the latter is provided in Fig. 1 in that recesses (11) of a support disc (15) to be described are adjusted in depth to the permissible suspension path.
  • the angle of rotation of the coupling is greater, the lower the inclination of the side surfaces (9a) and the longer this, i.e. the higher the projections (9).
  • the couplings can be used with very different properties, e.g. B. hard or soft, create. With a slope of 10! are, if the sprockets are conveniently about half the diameter of the clutch disc (14), to achieve angles of rotation of up to 30 °. It is advantageous that the clutch works in the same way in both directions of rotation, with all spring assemblies being acted on simultaneously.
  • the toothing is completely free of play and self-adjusting. It is also insensitive to fretting.
  • the tension of the spring elements (8) can be regulated by adjusting screws, which is necessary in the event of the springs settling, but is also desirable for changing the characteristics.
  • the characteristics of the clutch can also be regulated per se by changing the spring elements assembled to form spring assemblies, with stronger or weaker disc springs or combinations of the two being used.
  • a support disc (15) is arranged between the clutch disc (14) and the spring elements (8), which covers all spring assemblies and by pins (16) which engage in the bolts (10) relative to the secondary part (5) is fixed against rotation.
  • the support disc is provided with recesses (17) which serve as stops for the suspension travel.
  • the support disk (15) carries seals (12 and 18) on the inside and outside, which divide the coupling into two oil spaces, the toothing (6) acting as a throttle.
  • the support disc (15) is designed as an axial bearing for the clutch disc (14), whereby the friction to which the clutch disc (14) is exposed by the springs is considerably reduced.
  • the primary part (1) is connected to the hub (19) of the input and output shafts by means of a double-jointed coupling, which enables compensation of shaft misalignment in the radial and axial directions without the use of other means.
  • the housing (2) and the cover (3) of the secondary part (5) are provided with cooling fins (17). To achieve a twofold twist, it may be possible to connect two couplings of the type shown in FIG. 1 with the secondary parts (5).
  • two concentrically, ring-shaped coupling disks (20 and 21) are arranged between the primary part (1) and the housing shell (2) of the secondary part (5) axially next to one another, of which the disc (20) inside by a Teeth (6) are non-rotatably and axially displaceably connected to the primary part (1) and the disk (21) is non-rotatably and axially displaceably connected to the housing jacket (2) by means of a toothing (22).
  • the clutch disks (20 and 21) are provided approximately in the middle between the outer and inner diameter, each with a ring of axially extending projections (9) with oblique side surfaces (9a), between which frustoconical roller bodies (25 ) are located, which are held by axes (26) in a cage (27).
  • a toothing (28) is arranged, into which two guide gears (29) arranged in the cage (27) engage.
  • the use of rolling elements on the side surfaces of the projections reduces the friction between the clutch discs (20, 21).
  • the coupling is provided with a circulation of damping fluid in a special way.
  • the support disc (15) is provided with a throttle opening (30) below the center of the axis.
  • the support disc (15) forms a space on the left (high-pressure space) and a space (low-pressure space) on the right of the support disc.
  • Fig. 5 denotes - as in Fig. 1 - (1) the primary part, (14) the clutch disc and (15) the ring-shaped support disc resting thereon, which covers the spring elements (8) which rest on bolts (10 ) are led inside.
  • the support disc (15) is provided on the inside and in an analogous manner also on the outside with radial seals (18), by means of which it is sealed off from the housing or the primary part (1). It divides the clutch interior into the right chamber (41), which contains the spring elements (8) and into the left chamber (42), in which the clutch disc (14) with the projections (9) is arranged.
  • the damping fluid flows via the toothing (6) and the toothing on the coupling part (14) (not designated) from the right into the left chamber, the toothing acting as a throttle.
  • this flow path is interrupted by an axially acting seal (43) and the support plate (15) and the clutch plate (14) are provided with holes (44 and 45) at the locations of the bolts (10) , through which the damping fluid can now flow.
  • Pipe-like control parts (46) are arranged in the bores (45) of the support disk and carry a radial seal (47) at the outer end, which slides in the cylindrical recesses (48) of the bolts (10). Perpendicular to the pin axis are offset in the direction of the openings, radial throttle openings (49) are arranged on vertical planes and lead into the interior of the chamber (41).
  • the throttle openings (49) are each connected to channels (50) leading to the outside of the coupling, at the ends of which there are regulating screws (51) (only one shown), through which the flow through the openings and thus the damping of the coupling are regulated can be. Similar to FIG. 1, the throttle openings (49) are closed one after the other during a stroke movement of the coupling part or the support disk by the radial seal (47) of the control parts (46), their cross section also being able to be changed by means of regulating screws (51).
  • a tubular control part (33) is arranged on the clutch disc (14), which carries a radial seal (34) at the outer end. This seal slides during the working stroke on the cylindrical hub surface (35) of the primary part (1).
  • a plurality of radial throttle openings (36) are arranged on the circumference on a plane perpendicular to the axis, which start from the axially directed channels (37) leading to the outside, the throttle openings being able to be changed from the outside by means of regulating screws (38) . It is thus possible to influence the flow of the damping fluid over the entire torque curve without dismantling the clutch.
  • a conically increasing surface (35a) and then a cylindrical hub surface (35) is arranged, which again has throttle openings (36) at the end.
  • the flow becomes smaller and then completely closed, whereupon only, as in FIG. 6, the flow through the channels (37) and the throttle openings (36) takes place, which can be influenced by regulating screws (38).
  • regulating screws (38) With this regulation e.g. a damping characteristic can be achieved that is only kinked in the upper part.
  • a pair of seals (39, 40) is provided regardless of the aforementioned throttling method to the right of the clutch disc in the end position, which is closed when the clutch is in the zero position. It has the purpose of briefly interrupting the flow through the toothing when the torque is reversed (zero crossing), which is advantageous in the case of a specific type of design of the projections (9).
  • the primary part as in FIG. 1, is denoted by (1)
  • the reference number (5) denotes the secondary part
  • the clutch disc which is rotatably and axially displaceable via rolling elements (52) the primary part (1) is connected.
  • rings of axially extending projections (9) are arranged, between which there are rolling elements (25) which are guided in the cage (27).
  • the rolling elements (52) are also held in a cage (53) which is axially fixed to the outer cage (27) by means of bolts (54) and is relatively displaceably connected tangentially via longitudinal slots (55).
  • the clutch disc (14) When a torque is introduced into the primary part (1), the clutch disc (14) is carried along and axially displaced by the rolling elements (25), which lie between the projections (9), pressure exerted on the clutch disc (14) by the axial component Spring elements (8) is exercised.
  • the clutch disc (14) moves axially under the influence of external forces until an equilibrium has been established between these and the spring forces.
  • the cages (27 and 53) with the rolling elements (25) and the rolling elements (52) cover half the distance that the. Clutch disc (14) executes. The different tangential path of the two cages is compensated for by longitudinal slots (55) on the cage (53).

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Mechanical Operated Clutches (AREA)
  • Toys (AREA)
  • Adornments (AREA)
  • Stringed Musical Instruments (AREA)

Description

Die Erfindung betrifft eine drehelastische, schwingungsdämpfende Wellenkupplung nach dem Oberbegriff des Patentanspruches 1.The invention relates to a torsionally flexible, vibration-damping shaft coupling according to the preamble of claim 1.

Eine solche Wellenkupplung ist aus der DE-A-3148338 bekannt. Es sind (z.B. nach der DE-A-24 44 787 und DE-B-30 33 302) Kupplungen bekannt, bei denen ° zwischen einem Primär- und einem Sekundärteil radial gerichtete, durch Zwischenstücke eingespannte Blattfederpakete angeordnet sind, zwischen denen sich zwecks Dämpfung ölgefüllte Kammern befinden, wobei das ÖI bei Belastung von einer Kammer zur anderen gepreßt wird.Such a shaft coupling is known from DE-A-3148338. Couplings are known (for example according to DE-A-24 44 787 and DE-B-30 33 302) in which ° are arranged between a primary and a secondary part radially directed leaf spring assemblies clamped by intermediate pieces, between which there are for the purpose of damping Oil-filled chambers are located, the oil being pressed from one chamber to another when loaded.

Gemäß der US-A-25 13 379 ist eine Ausführung bekannt, bei der in Umfangsrichtung zur Drehachse tangential gerichtete Schraubenfedern angeordnet sind, die teilweise von topfartig ineinander schiebbaren Hülsen umgeben sind, durch deren Öffnungen das Dämpfungsöl strömt. Alle diese Konstruktionen lassen nur geringe Winkelausschläge zu und sind im Aufbau sehr kompliziert.According to US-A-25 13 379, an embodiment is known in which helical springs are arranged which are tangential in the circumferential direction to the axis of rotation and are partially surrounded by sleeves which can be pushed into one another like a pot and through whose openings the damping oil flows. All of these constructions allow only small angular deflections and are very complicated to set up.

Durch die DE-A-32 28 673 A-1 ist ein für die Anwendung bei Fahrzeug-Reibungskupplungen bestimmter Drehschwingungsdämpfer bekannt, bei dem die Drehmomentübertragung vom wellenartig ausgebildeten Primärteil auf den von ihm getragenen etwa trommelartigen Sekundärteil über einen darin angeordneten ringförmigen Kupplungskörper erfolgt, der mit einer Längsverschiebungen zulassenden Schubeinrichtung (Trapezgewinde) in den Primärteil eingreift und mit dem Umfang des Sekundärteils durch eine Axialverzahnung verschiebbar verbunden ist, wobei sich beiderseits des Kupplungskörpers je eine Tellerfeder befindet, die sich an der Wandung des Sekundärteils abstützt.DE-A-32 28 673 A-1 discloses a torsional vibration damper intended for use in vehicle friction clutches, in which the torque is transmitted from the shaft-shaped primary part to the approximately drum-like secondary part carried by it via an annular coupling body arranged therein, which engages with a thrust device (trapezoidal thread) allowing longitudinal displacements and is slidably connected to the periphery of the secondary part by means of axial toothing, with a plate spring on each side of the coupling body, which is supported on the wall of the secondary part.

Diese Art der Anordnung und der Beaufschlagungsweise der Federn ermöglicht zwar größere Winkelausschläge zwischen Primär- und Sekundärteil als bei den eingangs genannten Kupplungen; jedoch ist man durch die kleinstmögliche Steigung des Gewindes eingeschränkt, dessen Selbsthemmungsgrenze nicht erreicht werden darf.This type of arrangement and the way in which the springs are acted upon allows larger angular deflections between the primary and secondary parts than in the couplings mentioned at the beginning; however, one is limited by the smallest possible pitch of the thread, the self-locking limit of which must not be reached.

Bei einer solchen Bauart ist bei jeder Drehrichtung immer nur eine Tellerfeder in Aktion, während die andere unbeteiligt bleibt. Dies muß als eine schlechte Ausnutzung des vorhandenen Federvolumens angesehen werden, welche den Nutzwert der Kupplung stark beeinträchtigt. Die wechselweise Beanspruchung der Federn bei Drehrichtungsumkehr bedingt auch eine erhebliche Vorspannung der Federn, die größer sein muß als die Betriebsbeanspruchung, wodurch dem Bereich der wirksamen Verdrehung weitere Grenzen gesetzt sind. Infolge der unmittelbaren Nähe des Kupplungskörpers zu den Tellerfedern kann durch Abrieb verunreinigtes Dämpfungsöl an das Gewinde gelangen, was zu einem vorzeitigen Verschleiß der Verschiebeeinrichtung und damit zu einer Verkürzung der Lebensdauer führen muß. Grundsätzlich unterliegen Kupplungsglieder, deren Schrägflächen tangential zur Drehachse liegen, wie im Falle der genannten DE-B-32 28 673 A1, auch einem nicht zu beseitigenden Verdrehspiel, durch das bei einer Drehmomentumkehr Geschwindigkeitsstöße erzeugt werden, die einen sehr schädlichen Einfluß auf die Kupplung und die angeschlossenen Maschinen ausüben.With such a design, only one disc spring is in action in each direction of rotation, while the other remains uninvolved. This must be viewed as poor utilization of the existing spring volume, which has a major impact on the usefulness of the clutch. The alternating loading of the springs when the direction of rotation is reversed also requires a considerable preload of the springs, which must be greater than the operating load, which places further limits on the range of effective rotation. As a result of the immediate proximity of the coupling body to the disc springs, damping oil contaminated by abrasion can reach the thread, which must lead to premature wear of the displacement device and thus to a shortening of the service life. Basically, coupling members, the inclined surfaces of which are tangent to the axis of rotation, as in the case of the aforementioned DE-B-32 28 673 A1, are also subject to a torsional backlash which cannot be eliminated, by which speed shocks are generated when the torque is reversed, which have a very harmful influence on the coupling and exercise the connected machines.

Aus der eingangs genannten DE-A-31 48 338 ist eine Wellenkupplung in der Art einer Drehschwingungsabsorptionseinrichtung bekannt, bei der ein mit ÖI beaufschlagtes Gehäuse mit einer Lamellenreibkupplung vorgesehen ist, deren Lamellen auf einer Seite mit einem Tellerfederpaar beaufschlagt ist und auf der anderen Seite axial an einem Kupplungsring anliegt, der aus axial in einer Verzahnung des Gehäuses geführt ist und an dem Primärteil der Kupplung mit axial vorspringenden Zähnen mit schrägen Flanken anliegt, die in korrespondierende, gebogene Ausnehmungen an der Stirnseite des Primärteiles eingreifen. Durch Verdrehen der beiden Kupplungsteile gegeneinander wird daher der Kupplungsring axial bewegt und drückt auf die Lamellenkupplung, die somit als Dämpfungsglied für Drehschwingungen wirkt. Da bei dieser Bauart nur ein Tellerfederpaar konzentrisch zur Abtriebswelle angeordnet ist, lassen sich mit einer solchen Ausführung nur relativ geringe Drehkräfte übertragen, wenn der Raumbedarf der Dämpfungseinrichtung nicht zu groß werden soll.From the aforementioned DE-A-31 48 338, a shaft coupling in the manner of a torsional vibration absorption device is known, in which an oil-loaded housing is provided with a multi-plate friction clutch, the plates of which are acted upon by a plate spring pair and axially on the other side abuts a coupling ring which is guided axially in a toothing of the housing and bears on the primary part of the coupling with axially projecting teeth with oblique flanks which engage in corresponding, curved recesses on the end face of the primary part. By rotating the two coupling parts against each other, the coupling ring is therefore moved axially and presses on the multi-plate clutch, which thus acts as an attenuator for torsional vibrations. Since only one pair of disc springs is arranged concentrically to the output shaft in this type of construction, only a relatively small torsional force can be transmitted with such a design if the space requirement of the damping device is not to be too great.

Die Erfindung hat sich die Aufgabe gestellt, eine Wellenkupplung dieser Art zu schaffen, die eine hohe spezifische Übertragungsfähigkeit besitzt und daher raumsparend ist, wobei der Übertragungsmechanismus, der die tangentiale Bewegung des Primärteils in eine Axialbewegung und von dort wieder in eine tangentiale Bewegung des Sekundärteils umsetzt, möglichst abriebfrei ist und das gesamte Federvolumen unabhängig von der Momentenrichtung voll ausnutzt.The object of the invention is to create a shaft coupling of this type which has a high specific transmission capacity and is therefore space-saving, the transmission mechanism which converts the tangential movement of the primary part into an axial movement and from there again into a tangential movement of the secondary part is as abrasion-free as possible and fully utilizes the entire spring volume regardless of the direction of the torque.

Zur Lösung dieser Aufgabe werden bei einer Wellenkupplung der eingangs genanntn Art die kennzeichnenden Merkmale des Patentanspruches 1 vorgesehen. Durch diese Ausgestaltung wird eine Wellenkupplung mit einer geringen Zahl von Einzelteilen erreicht, die raumsparend Pakete von Federelementen, insbesondere Tellerfedern aufnimmt, die innen auf Bolzen geführt werden. Diese Kupplung ist auch dadurch, daß die Nabe ganz in das Gehäuse hineinragt, sehr schmal.To solve this problem, the characterizing features of claim 1 are provided in a shaft coupling of the type mentioned. With this configuration, a shaft coupling with a small number of individual parts is achieved, which accommodates packets of spring elements, in particular disk springs, which are guided on the inside on bolts in a space-saving manner. This coupling is also very narrow in that the hub extends completely into the housing.

Durch die Anordnung der Stützscheibe wird erreicht, daß alle Federpakete gleichmäßig wirken und der Abrieb gering bleibt. Die Stützscheibe ist dabei zweckmäßig als Axiallager ausgebildet.The arrangement of the support disc ensures that all spring assemblies act evenly and the abrasion remains low. The support disk is expediently designed as an axial bearing.

Eine besonders günstige Ausführungsform der Erfindung besteht darin, daß zwischen dem Primärteil und dem Sekundärteil zwei Kupplungsscheiben angeordnet sind, die auf den einander zugewandten Seiten mit den Vorsprüngen versehen sind, wobei beiderseits des Scheibenpaares Pakete von Tellerfedern angeordnet sind. Dadurch, daß hier mehr Federn, also auf zwei Seiten der Kupplungsscheiben für die Verdrehung zur Verfügung stehen, wird ein entsprechend größe- _rer Verdrehwinkel erreicht. Ganz allgemein können die kranzartigen Vorsprünge mehr nach dem äußeren Durchmesser oder mehr nach dem inneren Durchmesser der Kupplungsscheiben hin verlegt werden, je nachdem, ob es bei der Auslegung auf ein höheres zu übertragendes Drehmoment und eine weniger große Verdrehung oder auf eine größere Verdrehung bei einem niedrigeren Drehmoment ankommt. Besonders ausgewogene Verhältnisse ergeben sich, wenn diese erfindungsgemäß etwa in der Mitte zwischen dem Außen- und dem Innendurchmesser der Kupplungsscheiben angeordnet sind.A particularly advantageous embodiment of the invention consists in that two clutch disks are arranged between the primary part and the secondary part, which are provided with the projections on the mutually facing sides, packages of disc springs being arranged on both sides of the pair of disks. The fact that more springs are available here for rotation, ie on two sides of the clutch discs, results in a correspondingly larger angle of rotation. In general, the wreath-like projections can more after outer diameter or more according to the inner diameter of the clutch discs, depending on whether the design is based on a higher torque to be transmitted and less rotation or a larger rotation at a lower torque. Particularly balanced ratios result if, according to the invention, these are arranged approximately in the middle between the outer and inner diameters of the clutch disks.

An das Dämpfungsverhalten von hochdrehelastischen Kupplungen mit Flüssigkeitsdämpfung können verschiedene, von Anwendungsfällen und Betriebszuständen abhängige Anforderungen gestellt werden.Various requirements can be placed on the damping behavior of highly torsionally flexible couplings with fluid damping, depending on applications and operating conditions.

So kann die Forderung bestehen, daß mit zunehmendem Drehmoment die Flüssigkeitsdämpfung ansteigen soll, oder/und beim Nulldurchgang, d.h. bei kleinem Drehmoment, eine größere Dämpfung erwünscht ist. Ferner ergibt sich bei schwingungstechnisch schwierigen Anlagen auch der Wunsch, die Dämpfung nachträglich zu verändern. Bei bekannten Kupplungen ist letzteres nur durch Austausch von Bauteilen mit veränderten Drosselöffnungen oder Spalten möglich.So there may be a requirement that the fluid damping should increase with increasing torque, and / or at zero crossing, i.e. with low torque, greater damping is desired. Furthermore, in systems with difficult vibrations, there is also the desire to change the damping subsequently. In known couplings, the latter is only possible by replacing components with modified throttle openings or gaps.

Eine vorteilhafte Weiterbildung der Erfindung sieht eine Einrichtung vor, durch die eine wahlweise feinfühlig steuerbare Dämpfung über den ganzen Drehmomentverlauf ermöglicht wird, wobei die Veränderung der Dämpfungscharakteristik entweder selbsttätig oder/und von außen her erfolgt. Dies wird dadurch erreicht, daß die Stützscheibe am Außenumfang und gegebenenfalls auch am Innenumfang mit Dichtungen versehen ist und das Gehäuse in zwei Kammern unterteilt, wobei in der Nähe der Drehachse eine Drosselöffnung zwischen den Kammern vorgesehen ist. An der Durchflußöffnung zwischen den Kammern kann ein am äußeren Ende mit einer Radialdichtung versehenes, rohrartiges Steuerteil vorgesehen sein, welches mit entsprechenden, im Primär-oder Sekundärteil gegebenen, axial gerichteten Kanälen zusammenwirkt, die mit mehreren auf achsparallelen Ebenen hintereinanderliegenden, ins Kupplungsinnere führenden Drosselöffnungen versehen sind, welche von der Radialdichtung während des Arbeitshubes überstrichen werden, wobei mindestens eine Drosselöffnung von der Stirnseite der Kupplung her mit einer Regelschraube o.dgl. in ihrem Querschnitt veränderbar ist.An advantageous development of the invention provides a device by means of which an optionally finely controllable damping is made possible over the entire torque curve, the damping characteristics being changed either automatically or / and from the outside. This is achieved in that the support disk is provided on the outer circumference and possibly also on the inner circumference with seals and divides the housing into two chambers, a throttle opening being provided between the chambers near the axis of rotation. At the flow opening between the chambers, a tubular control part provided with a radial seal at the outer end can be provided, which cooperates with corresponding axially directed channels in the primary or secondary part, which channels are provided with a plurality of throttle openings lying one behind the other on axially parallel planes and leading into the coupling interior are which are swept by the radial seal during the working stroke, with at least one throttle opening from the front of the clutch or the like with a regulating screw. its cross section is changeable.

Um die Dämpfung von außen her beeinflussen zu können, besteht eine vorteilhafte Ausführung darin, daß mindestens eine Drosselöffnung von der Stirnseite der Kupplung her mit einer Regelschraube im Querschnitt veränderbar ist. Die Regelschraube kann auch als selbsttätig arbeitendes, druckabhängiges Ventil ausgebildet sein, welches von außen nachstellbar ist.In order to be able to influence the damping from the outside, an advantageous embodiment consists in that at least one throttle opening can be changed in cross-section from the front side of the coupling with a regulating screw. The regulating screw can also be designed as an automatically operating, pressure-dependent valve, which can be adjusted from the outside.

Eine weitere günstige Ausführung der Erfindung, durch welche ebenfalls die Dämpfungscharakteristik verändert werden kann, besteht darin, daß die Radialdichtung nur in Teilbereichen des Arbeitshubes wirksam ist. Je nach der Bauweise der Kupplung kann als Durchflußöffnung zwischen den Kammern, z.B. die Kupplungsverzahnung zwischen der Kupplungsscheibe und dem Primärteil dienen, wobei das Steuerteil an der Kupplungsscheibe angeordnet ist.Another favorable embodiment of the invention, by means of which the damping characteristic can also be changed, is that the radial seal is only effective in partial areas of the working stroke. Depending on the design of the coupling, a flow opening between the chambers, e.g. the clutch teeth between the clutch disc and the primary part serve, the control part being arranged on the clutch disc.

Eine andere günstige Ausführungsform besteht darin, daß als Durchflußöffnung zwischen den Kammern Bohrungen in der Stützscheibe und in der anliegenden Kupplungsscheibe im Bereich der Bolzen liegen, an denen die Federelemente gehalten sind, wobei an jeder Bohrung der Stützscheibe ein Steuerteil angeordnet ist.Another favorable embodiment consists in that as a flow opening between the chambers there are bores in the support disk and in the adjacent clutch disk in the region of the bolts on which the spring elements are held, with a control part being arranged in each bore of the support disk.

Drehelastische Kupplungen, deren Wirkungsweise darauf beruht, daß unter Last eine Umfangskraft in eine Axialkraft und von da wieder in eine Umfangskraft umgesetzt wird, haben, sofern die damit einhergehende Axialschiebung über reibungsbehaftete Kupplungsverbindungen erfolgt, den Nachteil, daß die Reibwerte Schwankungen unterliegen können, die unter anderem von der spezifischen Belastung der Werkstoffpaarung, der Schmiermittelzufuhr und der Geleitgeschwindigkeit abhängen. Sollen Kupplungen der erfindungsgemäßen Art feinfühlig auch bei hohen Frequenzen ansprechen, so kann es unter bestimmten Voraussetzungen zu einem Ruckgleiten kommen, das den gleichmäßigen Kraftverlauf stört.Torsionally flexible couplings, the mode of operation of which is based on the fact that a circumferential force is converted into an axial force under load and from there back into a circumferential force, the disadvantage, provided that the associated axial displacement takes place via coupling connections subject to friction, is that the coefficients of friction can be subject to fluctuations that occur under depend, among other things, on the specific load on the material pairing, the lubricant supply and the speed of the escort. If clutches of the type according to the invention are to respond sensitively even at high frequencies, then under certain conditions sticking back can occur which interferes with the uniform development of the force.

Vorteilhaft ist es daher, Gleitreibung vollkommen zu vermeiden und die Verzahnung an der Kupplungsscheibe durch eine Kugelwälzverbindung zu ersetzen, wobei auf die aufwendige Steuerung der Kugeln, wie dies bei bekannten Konstruktionen von Gleichlaufgelenken üblich ist, verzichtet wird. Dabei kann davon ausgegangen werden, daß das Sekundärteil mit seinen axialen Vorsprüngen räumlich feststeht, während sich die Kupplungsscheibe unter der Wirkung des Drehmomentes axial verschiebt. Werden zwischen den axialen Vertiefungen der Kupplungsscheibe und des Sekundärteils Rollkörper, die in einem Käfig geführt werden, angeordnet, so stellt sich dieser Käfig unter Last zwangsläufig auf den halben axialen Weg der Kupplungsscheibe ein, d.h. auf den gleichen axialen Weg, den auch die Kugeln der Kupplungsverbindung zurücklegen.It is therefore advantageous to completely avoid sliding friction and to replace the toothing on the clutch disc by a ball and roller connection, with the complex control of the balls, as is customary in known designs of constant velocity joints, being dispensed with. It can be assumed that the secondary part with its axial projections is spatially fixed, while the clutch disc moves axially under the effect of the torque. If rolling elements, which are guided in a cage, are arranged between the axial recesses of the clutch disc and the secondary part, this cage inevitably adjusts to half the axial path of the clutch disc under load, i.e. in the same axial path as the balls of the coupling connection.

In weiterer Ausgestaltung der Erfindung wird daher vorgesehen, den Bewegungsablauf des zwangsgeführten äußeren Käfigs zu nutzen, indem der Käfig der Kugelwälzverbindung über Bolzen o.dgl. mit dem äußeren Käfig der Rollkörper verbunden wird, so daß sich beide Käfige gemeinsam axial verschieben und die unterschiedlichen tangentialen Wege durch Längsschlitze am inneren Käfig ausgeglichen werden.In a further embodiment of the invention it is therefore provided to use the movement sequence of the positively guided outer cage by the cage of the ball rolling connection via bolts or the like. is connected to the outer cage of the rolling element, so that both cages move axially together and the different tangential paths are compensated for by longitudinal slots on the inner cage.

In den Zeichnungen sind verschiedene Ausführungsbeispiele der Erfindung dargestellt, die in der folgenden Beschreibung erläutert werden. Es zeigen:Various exemplary embodiments of the invention are illustrated in the drawings and are explained in the following description. Show it:

  • Fig. 1 im Längsschnitt eine Kupplung mit einseitigen Federpaketen, mit Stützscheibe und mit einer doppelgelenkigen Kupplung an der Nabe,1 is a longitudinal section of a clutch with spring assemblies on one side, with a support disk and with a double-jointed clutch on the hub,
  • Fig. 2 eine Kupplung mit zwei Kupplungsscheiben und beidseitigen Federpaketen und Rollkörpern im Längsschnitt,2 shows a clutch with two clutch disks and spring assemblies on both sides and rolling elements in longitudinal section,
  • Fig. 3 den Querschnitt A-B durch die Kupplung nach Fig. 2,3 shows the cross section A-B through the coupling according to FIG. 2,
  • Fig, 4a bis d Abwicklungen der kranzartig angeordneten Vorsprünge in verschiedener Ausführungsform,4a to d developments of the ring-shaped projections in various embodiments,
  • Fig. 5 die Einzelheit "B.. der Fig. 1,5 shows the detail " B .. of Fig. 1,
  • Fig. 6 eine Einzelheit der Ausbildung einer Variante der Fig. 1,6 shows a detail of the design of a variant of FIG. 1,
  • Fig. 7 eine andere Ausführung der Einzelheit der Variante der Fig. 1,7 shows another embodiment of the detail of the variant of FIG. 1,
  • Fig. 8 eine weitere Einzelheit der Variante der Fig. 1,8 shows a further detail of the variant of FIG. 1,
  • Fig. 9 eine Einzelheit einer anderen Variante der Fig. 1 undFig. 9 shows a detail of another variant of Fig. 1 and
  • Fig. 10 den Schnitt C-D durch Fig. 9.10 shows the section C-D through FIG. 9.

In Fig. 1 bezeichnete (1) den Primärteil, welcher mit dem Gehäuse (2) verbunden ist, das durch den Deckel (3) verschlossen ist. Am Deckel (3) ist der Sekundärteil (5) gehalten. Der Sekundärteil (5) ist mit einem Flansch (5a) zum Anschluß an die anzutreibende oder auch antreibende Maschine versehen. Zwischen dem Primärteil (1) und dem Sekundärteil (5) ist neben der Wandung des letzteren eine konzentrische, ringartige Kupplungsscheibe (14) angeordnet.In Fig. 1 designated (1) the primary part, which is connected to the housing (2), which is closed by the cover (3). The secondary part (5) is held on the cover (3). The secondary part (5) is provided with a flange (5a) for connection to the machine to be driven or also driven. Between the primary part (1) and the secondary part (5), a concentric, ring-like clutch disc (14) is arranged next to the wall of the latter.

Bei Einleitung eines Drehmomentes in den Primärteil (1) wird die Kupplungsscheibe (14) mitgenommen und durch die Vorsprünge (9) auch der Sekundärteil (5). Gleichzeitig gleiten die Vorsprünge, deren Seitenflächen (9a) (s. Fig. 4a bis 4d) eine Neigung von z.B. 20° bis 40° haben, in Umfangsrichtung aufeinander auf, wobei durch die Axialkomponente der Aufgleitkraft Druck auf die Kupplungsscheibe (14) und über diese auf die zu einem Federpaket zusammengesetzten Federelement (8) ausgeübt wird, die als Tellerfedern ausgebildet sind. Dies kann bei steigendem Drehmoment so lange erfolgen, bis es, je nachdem, wie die Kupplung ausgelegt ist, entweder zu einem Durchrutschen der Vorsprünge (9) kommt, d.h. die Kupplung arbeitet als Überlastschutz für die angeschlossene Maschine, oder es werden Anschläge für die Begrenzung des Federweges vorgesehen, bei deren Erreichung die Kupplung dann drehstarr wirkt, d.h. es tritt ein Schutz der Kupplung ein. Letzteres ist in Fig. 1 dadurch vorgesehen, daß Ausnehmungen (11) einer noch zu beschreibenden Stützscheibe (15) in ihre Tiefe auf den zulässigen Federungsweg abgestellt sind.When a torque is introduced into the primary part (1), the clutch disc (14) is taken along and through the projections (9) also the secondary part (5). At the same time, the projections slide, the side surfaces (9a) (see Fig. 4a to 4d) an inclination of e.g. Have 20 ° to 40 °, in the circumferential direction on each other, the axial component of the sliding force exerting pressure on the clutch disc (14) and via this on the spring element (8) assembled to form a spring assembly, which are designed as disc springs. With increasing torque, this can take place until, depending on the design of the coupling, the projections (9) either slip, i.e. the coupling works as overload protection for the connected machine, or stops are provided for limiting the spring travel, when reached the coupling then acts in a torsionally rigid manner, i.e. the clutch is protected. The latter is provided in Fig. 1 in that recesses (11) of a support disc (15) to be described are adjusted in depth to the permissible suspension path.

Der Verdrehwinkel der Kupplung ist um so größer, je geringer die Neigung der Seitenflächen (9a) und je länger diese, d.h. je höher die Vorsprünge (9) sind. Bei entsprechender Abstimmung der Neigung und Länge dieser Seitenflächen und der Charakteristik der Federpakete lassen sich die Kupplungen mit ganz verschiedenen Eigenschaften, z. B. harte oder weiche, schaffen. Bei einer Neigung von 10! sind, wenn die Zahnkränze in günstiger Weise etwa auf dem halben Durchmesser der Kupplungsscheibe (14) liegen, Drehwinkel bis zu 30° zu erreichen. Vorteilhaft ist dabei, daß die Kupplung nach beiden Drehrichtungen in der gleichen Weise arbeitet, wobei jeweils alle Federpakete gleichzeitig beaufschlagt werden. Die Verzahnung ist völlig spielfrei und selbstnachstellend. Sie ist auch unempfindlich gegen Reibverschleiß. Dazu kommt auch, daß sie außerhalb des Bereiches der Tellerfedern liegt, bei denen gegebenenfalls Verschleiß auftreten kann. Die Spannung der Federelemente (8) kann durch Nachstellschrauben geregelt werden, was im Falle von Setzungen der Federn notwendig, aber auch zur Veränderung der Charakteristik erwünscht ist. Außerdem ist die Charakteristik der Kupplung auch durch Veränderung der zu Federpaketen zusammengesetzten Federelemente an sich regelbar, wobei stärkere oder schwächere Tellerfedern oder auch Kombinationen beider in Anwendung kommen können.The angle of rotation of the coupling is greater, the lower the inclination of the side surfaces (9a) and the longer this, i.e. the higher the projections (9). With appropriate coordination of the inclination and length of these side surfaces and the characteristics of the spring assemblies, the couplings can be used with very different properties, e.g. B. hard or soft, create. With a slope of 10! are, if the sprockets are conveniently about half the diameter of the clutch disc (14), to achieve angles of rotation of up to 30 °. It is advantageous that the clutch works in the same way in both directions of rotation, with all spring assemblies being acted on simultaneously. The toothing is completely free of play and self-adjusting. It is also insensitive to fretting. There is also the fact that it lies outside the area of the disc springs, where wear may occur. The tension of the spring elements (8) can be regulated by adjusting screws, which is necessary in the event of the springs settling, but is also desirable for changing the characteristics. In addition, the characteristics of the clutch can also be regulated per se by changing the spring elements assembled to form spring assemblies, with stronger or weaker disc springs or combinations of the two being used.

In Fig. 1 ist zwischen der Kupplungsscheibe (14) und den Federelementen (8) eine Stützscheibe (15) angeordnet, welche alle Federpakete überdeckt und durch Stifte (16), die in die Bolzen (10) eingreifen, gegenüber dem Sekundärteil (5) gegen Drehung fixiert ist. Die Stützscheibe ist mit Ausnehmungen (17) versehen, die als Anschläge für den Federungsweg dienen. Die Stützscheibe (15) trägt innen und außen Dichtungen (12 und 18), die die Kupplung in zwei Ölräume unterteilen, wobei die Verzahnung (6) als Drossel wirkt. Auf der anderen Seite ist die Stützscheibe (15) als Axiallager für die Kupplungsscheibe (14) ausgebildet, wodurch die Reibung, der die Kupplungsscheibe (14) durch die Federn ausgesetzt ist, erheblich vermindert wird. Der Primärteil (1) ist durch eine doppelgelenkige Kupplung mit der Nabe (19) der Antriebs- und Abtriebswelle verbunden, wodurch ohne Einschaltung anderer Mittel ein Ausgleich von Wellenversatz in radialer und axialer Richtung möglich ist. Zur besseren Kühlung ist das Gehäuse (2) und der Deckel (3) des Sekundärteils (5) mit Kühlrippen (17) versehen. .Zur Erzielung einer doppelt so großen Verdrehung ist es gegebenenfalls möglich, je zwei Kupplungen der Bauart von Fig. 1 mit den Sekundärteilen (5) miteinander zu verbinden.In Fig. 1, a support disc (15) is arranged between the clutch disc (14) and the spring elements (8), which covers all spring assemblies and by pins (16) which engage in the bolts (10) relative to the secondary part (5) is fixed against rotation. The support disc is provided with recesses (17) which serve as stops for the suspension travel. The support disk (15) carries seals (12 and 18) on the inside and outside, which divide the coupling into two oil spaces, the toothing (6) acting as a throttle. On the other hand, the support disc (15) is designed as an axial bearing for the clutch disc (14), whereby the friction to which the clutch disc (14) is exposed by the springs is considerably reduced. The primary part (1) is connected to the hub (19) of the input and output shafts by means of a double-jointed coupling, which enables compensation of shaft misalignment in the radial and axial directions without the use of other means. For better cooling, the housing (2) and the cover (3) of the secondary part (5) are provided with cooling fins (17). To achieve a twofold twist, it may be possible to connect two couplings of the type shown in FIG. 1 with the secondary parts (5).

In den Fig. 2 und 3 sind zwischen dem Primärteil (1) und dem Gehäusemantel (2) des Sekundärteils (5) axial nebeneinanderliegend zwei konzentrisch, ringartig ausgebildete Kupplungsscheiben (20 und 21) angeordnet, von denen die Scheibe (20) innen durch eine Verzahnung (6) drehfest und axial verschiebbar mit dem Primärteil (1) und die Scheibe (21) durch eine Verzahnung (22) drehfest und axial verschiebbar mit dem Gehäusemantel (2) verbunden sind. An den einander zugekehrten Seiten sind die Kupplungsscheiben (20 und 21) etwa in der Mitte zwischen Außen- und Innendurchmesser mit je einem Kranz von sich axial erstreckenden Vorsprüngen (9) mit schrägen Seitenflächen (9a), versehen, zwischen denen sich kegelstumpfartige Rollenkörper (25) befinden, die durch Achsen (26) in einem Käfig (27) gehalten sind. An zwei diametral gegenüberliegenden Stellen (s. Fig. 3) der Kränze ist je eine Verzahnung (28) angeordnet, in die zwei im Käfig (27) angeordnete Führungszahnräder (29) eingreifen. Die Anwendung von Rollkörpern auf den Seitenflächen der Vorsprünge setzt die Reibung zwischen den Kupplungsscheiben (20, 21) herab. Beidseitig neben der Kupplungsscheiben (20 und 21) sind Pakete von als Tellerfedern ausgebildeten Federelementen (8) angeordnet, die von Bolzen (10) gehalten werden. Zwischen die Kupplungsscheibe (20) und die Federelemente (8) der rechten Seite ist wieder, wie in Fig. 1, eine Stützscheibe (15) eingeschaltet, die als Axiallager ausgebildet ist. Sie ist am Außenumfang mit einer Dichtung (12) versehen. Sie und die Kupplungsscheibe (21) sind auch wieder mit Anschlägen (11) zur Begrenzung der Verdrehung versehen. Bei Einleitung eines Drehmomentes werden die Federelemente (8) beider Seiten zugleich beaufschlagt, und zwar bei beiden Momentenrichtungen. Diese Ausführung ermöglicht gegenüber den von Fig. 1 einen größeren Verdrehwinkel.2 and 3, two concentrically, ring-shaped coupling disks (20 and 21) are arranged between the primary part (1) and the housing shell (2) of the secondary part (5) axially next to one another, of which the disc (20) inside by a Teeth (6) are non-rotatably and axially displaceably connected to the primary part (1) and the disk (21) is non-rotatably and axially displaceably connected to the housing jacket (2) by means of a toothing (22). On the sides facing each other, the clutch disks (20 and 21) are provided approximately in the middle between the outer and inner diameter, each with a ring of axially extending projections (9) with oblique side surfaces (9a), between which frustoconical roller bodies (25 ) are located, which are held by axes (26) in a cage (27). At two diametrically opposite points (see FIG. 3) of the rings, a toothing (28) is arranged, into which two guide gears (29) arranged in the cage (27) engage. The use of rolling elements on the side surfaces of the projections reduces the friction between the clutch discs (20, 21). Ne on both sides ben of the clutch discs (20 and 21) packages of spring elements (8) designed as disc springs are arranged, which are held by bolts (10). Between the clutch disc (20) and the spring elements (8) on the right side, as in FIG. 1, a support disc (15) is connected, which is designed as an axial bearing. It is provided with a seal (12) on the outer circumference. You and the clutch disc (21) are again provided with stops (11) to limit the rotation. When torque is applied, the spring elements (8) are acted upon on both sides at the same time, in both torque directions. This embodiment enables a larger angle of rotation than that of FIG. 1.

Die Kupplung ist in besonderer Weise mit einem Umlauf von Dämpfungsflüssigkeit versehen. Dazu ist hier die Stützscheibe (15) unterhalb der Achsmitte mit einer Drosselöffnung (30) versehen. Durch die Stützscheibe (15) wird links ein Raum (Hochdruckraum) und rechts der Stützscheibe ein Raum (Niederdruckraum) gebildet. Bei entsprechender Ölfüllung baut sich infolge der Pumpbewegung der Scheiben (20, 21) im HD-Raum ein Druck auf, der einen Übertritt des Öls durch die Drosselöffnung (30) in den ND-Raum bewirkt, von wo das Öl durch die zentrale Öffnung (23) austritt und von wo es durch eine Leitung (nicht gezeichnet) der Öffnung (24) des HD-Raumes wieder zugeführt wird, wobei die Ölumführung mittels einer externen Pumpe und eines zwischengeschalteten Öltanks erfolgt, was besonders bei Kupplungen für große Antriebsleistungen erforderlich ist, die sehr heiß werden können.The coupling is provided with a circulation of damping fluid in a special way. For this purpose, the support disc (15) is provided with a throttle opening (30) below the center of the axis. The support disc (15) forms a space on the left (high-pressure space) and a space (low-pressure space) on the right of the support disc. With a corresponding oil filling, a pressure builds up in the HP space due to the pumping movement of the disks (20, 21), which causes the oil to pass through the throttle opening (30) into the LP space, from where the oil passes through the central opening ( 23) emerges and from where it is fed back through a line (not shown) to the opening (24) of the high-pressure chamber, the oil bypassing being carried out by means of an external pump and an intermediate oil tank, which is particularly necessary for couplings for large drive powers that can get very hot.

In Fig. 4a bis d sind verschiedene Ausführungsformen der kranzartigen Vorsprünge im Querschnitt in Laststellung dargestellt:

  • a) zeigt Vorsprünge (9) mit Seitenflächen (9a) mit gleichem Neigungswinkel auf der Vorder- und Rückseite (Winkel ca. 20°),
  • b) zeigt Vorsprünge (9) mit Seitenflächen (9a und 9b) von unterschiedlichem Neigungswinkel (Winkel 20°/45°) auf der Vorder- und Rückseite, wodurch die Kupplung in der einen Drehrichtung eine weichere und in der anderen eine härtere Charakteristik erhält,
  • c) zeigt ein Profil wie in a), jedoch mit Rollkörpern (25) zwischen den Kränzen, die durch Achsen (26) in einem Käfig (27) gehalten sind. Hierdurch wird die Reibung zwischen den Verzahnungen herabgesetzt,
  • d) zeigt im oberen Kranz ein Profil mit Seitenflächen (9a) von 20°, die nach der Spitze hin stärker (auf 45°) ansteigen, (9c) wodurch sich bei steigender Belastung eine progressive Charakteristik der Kupplung ergibt. Im unteren Kranz sind die Rollkörper (25) in Mulden gehalten. Es besteht auch die Möglichkeit, bei der Ausführung nach c) die Seitenflächen (9a) mit Verzahnungen zu versehen, an denen die ebenfalls mit Verzahnungen versehenen Rollkörper abrollen können.
4a to d show different embodiments of the ring-like projections in cross section in the load position:
  • a) shows projections (9) with side surfaces (9a) with the same angle of inclination on the front and back (angle about 20 °),
  • b) shows projections (9) with side surfaces (9a and 9b) of different angles of inclination (angle 20 ° / 45 °) on the front and rear, whereby the coupling receives a softer characteristic in one direction of rotation and a harder characteristic in the other,
  • c) shows a profile as in a), but with rolling elements (25) between the rings, which are held in a cage (27) by axes (26). This reduces the friction between the teeth,
  • d) shows in the upper rim a profile with side surfaces (9a) of 20 °, which increase more towards the tip (to 45 °), (9c) which results in a progressive characteristic of the coupling with increasing load. The rolling elements (25) are held in troughs in the lower ring. There is also the possibility, in the embodiment according to c), to provide the side surfaces (9a) with serrations on which the rolling elements, which are also provided with serrations, can roll.

In der Fig. 5 bezeichnet- wie in der Fig. 1 - (1) das Primärteil, (14) die Kupplungsscheibe und (15) die an dieser anliegende, ringförmige Stützscheibe, welche die Federelemente (8) abdeckt, die auf Bolzen (10) innen geführt sind. Die Stützscheibe (15) ist innen und in analoger Weise auch außen mit Radialdichtungen (18) versehen, durch die sie gegenüber dem Gehäuse bzw. dem Primärteil (1) abgedichtet ist. Sie teilt den Kupplungsinnenraum in die rechte Kammer (41), welche die Federelemente (8) enthält und in die linke Kammer (42), in welcher die Kupplungsscheibe (14) mit den Vorsprüngen (9) angeordnet ist.In Fig. 5 denotes - as in Fig. 1 - (1) the primary part, (14) the clutch disc and (15) the ring-shaped support disc resting thereon, which covers the spring elements (8) which rest on bolts (10 ) are led inside. The support disc (15) is provided on the inside and in an analogous manner also on the outside with radial seals (18), by means of which it is sealed off from the housing or the primary part (1). It divides the clutch interior into the right chamber (41), which contains the spring elements (8) and into the left chamber (42), in which the clutch disc (14) with the projections (9) is arranged.

Bei dieser Anordnung strömt die Dämpfungsflüssigkeit über die Verzahnung (6) und die Verzahnung am Kuppelteil (14) (nicht bezeichnet) von der rechten in die linke Kammer, wobei die Verzahnungen als Drossel wirken.In this arrangement, the damping fluid flows via the toothing (6) and the toothing on the coupling part (14) (not designated) from the right into the left chamber, the toothing acting as a throttle.

Zur Regelung der Dämpfung ist gemäß Fig. 5 dieser Strömungsweg durch eine axial wirkende Dichtung (43) unterbrochen und die Stützscheibe (15) sowie die Kupplungsscheibe (14) sind an den Stellen der Bolzen (10) mit Bohrungen (44 bzw. 45) versehen, durch die nunmehr die Dämpfungsflüssigkeit strömen kann. In den Bohrungen (45) der Stützscheibe sind rohrartige Steuerteile (46) angeordnet, welche am äußeren Ende eine Radialdichtung (47) tragen, die in den zylindrischen Ausnehmungen (48) der Bolzen (10) gleitet. Senkrecht zur Bolzenachse sind in Richtung der Öffnungen versetzt, auf senkrechten Ebenen radiale Drosselöffnungen (49) angeordnet, die ins Innere der Kammer (41) führen. Die Drosselöffnungen (49) sind je für sich mit nach außerhalb der Kupplung führenden Kanälen (50) verbunden, an deren Enden sich Regelschrauben (51) (nur eine gezeichnet) befinden, durch die der Durchfluß auf die Öffnungen und damit die Dämpfung der Kupplung geregelt werden kann. Ähnlich wie in Fig. 1 werden auch hier bei einer Hubbewegung des Kuppelteils bzw. der Stützscheibe durch die Radialdichtung (47) der Steuerteile (46) die Drosselöffnungen (49) nacheinander verschlossen, wobei ihr Querschnitt außerdem durch Regelschrauben (51) verändert werden kann.5, this flow path is interrupted by an axially acting seal (43) and the support plate (15) and the clutch plate (14) are provided with holes (44 and 45) at the locations of the bolts (10) , through which the damping fluid can now flow. Pipe-like control parts (46) are arranged in the bores (45) of the support disk and carry a radial seal (47) at the outer end, which slides in the cylindrical recesses (48) of the bolts (10). Perpendicular to the pin axis are offset in the direction of the openings, radial throttle openings (49) are arranged on vertical planes and lead into the interior of the chamber (41). The throttle openings (49) are each connected to channels (50) leading to the outside of the coupling, at the ends of which there are regulating screws (51) (only one shown), through which the flow through the openings and thus the damping of the coupling are regulated can be. Similar to FIG. 1, the throttle openings (49) are closed one after the other during a stroke movement of the coupling part or the support disk by the radial seal (47) of the control parts (46), their cross section also being able to be changed by means of regulating screws (51).

In den Fig. 6, 7 und 8 bezeichnet (1) das Primärteil und (14) wieder die Kupplungsscheibe, welche mit ihrer Verzahnung (6) drehfest und axial verschiebbar mit dem Primärteil (1) verbunden ist. Die Kupplungsscheibe (14) ist auch hier durch eine Dichtung gegenüber dem Gehäuse radial abgedichtet. In der Kammer (31) links des Kuppelteils sind die Federelemente (8) angeordnet, die innen durch die Bolzen (10) geführt sind. In der Kammer rechts von der Kupplungsscheibe (14) sind die, in Fig. 6 aber nicht gezeigten, Mitnehmer in Form von Vorsprüngen (9) angeordnet, die in entsprechende Elemente am Sekundärteil (5) eingreifen.6, 7 and 8 designate (1) the primary part and (14) again the clutch disc, which is connected to the primary part (1) in a rotationally fixed and axially displaceable manner by its toothing (6). The clutch disc (14) is also radially sealed from the housing by a seal. In the chamber (31) to the left of the dome part, the spring elements (8) are arranged, which are guided inside by the bolts (10). Arranged in the chamber to the right of the clutch disc (14) are the drivers (not shown in FIG. 6) in the form of projections (9) which engage corresponding elements on the secondary part (5).

Bei der Hubbewegung der Kupplungsscheibe (14) wird Dämpfungsflüssigkeit aus der Kammer (31) in die rechte Kammer durch die Verzahnung (6) gedrückt. Beim Nachlassen des Drehmomentes strömt sie wieder zurück. Für die Regelung der Dämpfung ist gemäß Fig. 6 an der Kupplungsscheibe (14) ein rohrartiges Steuerteil (33) angeordnet, das am äußeren Ende eine Radialdichtung (34) trägt. Diese Dichtung gleitet beim Arbeitshub auf der zylindrischen Nabenfläche (35) des Primärteils (1). Am Ende der Nabenfläche sind am Umfang auf einer Ebene senkrecht zur Achse mehrere radiale Drosselöffnungen (36) angeordnet, die von den axial gerichteten, nach außen führenden Kanälen (37) ausgehen, wobei die Drosselöffnungen durch Regulierschrauben (38) von außen her verändert werden können. Man hat damit die Möglichkeit, die Durchströmung der Dämpfungsflüssigkeit über den gesamten Drehmomentverlauf ohne Demontage der Kupplung zu beeinflussen.During the lifting movement of the clutch disc (14), damping fluid is pressed out of the chamber (31) into the right chamber through the toothing (6). When the torque decreases, it flows back again. 6, a tubular control part (33) is arranged on the clutch disc (14), which carries a radial seal (34) at the outer end. This seal slides during the working stroke on the cylindrical hub surface (35) of the primary part (1). At the end of the hub surface, a plurality of radial throttle openings (36) are arranged on the circumference on a plane perpendicular to the axis, which start from the axially directed channels (37) leading to the outside, the throttle openings being able to be changed from the outside by means of regulating screws (38) . It is thus possible to influence the flow of the damping fluid over the entire torque curve without dismantling the clutch.

In Fig. 7 ist abweichend von Fig. 6 erst eine konisch ansteigende Fläche (35a) und dann eine zylindrische Nabenfläche (35) angeordnet, die am Ende wieder Drosselöffnungen (36) aufweist. In diesem Fall findet zunächst eine freie Durchströmung durch den Zwischenraum zwischen der Dichtung (34) und der konischen Fläche (35a) statt. Später wird der Durchfluß kleiner, und dann ganz verschlossen, worauf nur noch, wie in Fig. 6, die Strömung durch die Kanäle (37) und die Drosselöffnungen (36) erfolgt, die durch Regelschrauben (38) beeinflußt werden können. Mit dieser Regelung kann z.B. eine Dämpfungscharakteristik erzielt werden, die nur im oberen Teil abgeknickt ist.In Fig. 7, in contrast to Fig. 6, first a conically increasing surface (35a) and then a cylindrical hub surface (35) is arranged, which again has throttle openings (36) at the end. In this case, there is first a free flow through the space between the seal (34) and the conical surface (35a). Later, the flow becomes smaller and then completely closed, whereupon only, as in FIG. 6, the flow through the channels (37) and the throttle openings (36) takes place, which can be influenced by regulating screws (38). With this regulation e.g. a damping characteristic can be achieved that is only kinked in the upper part.

In Fig. 8 ist unabhängig von den vorgenannten Drosselverfahren rechts der Kupplungsscheibe in der Endlage ein Paar von Dichtungen (39, 40) vorgesehen, das bei Nullstellung der Kupplung geschlossen ist. Es hat den Zweck, bei Drehmomentumkehr (Nulldurchgang) die Strömung durch die Verzahnung kurzzeitig zu unterbrechen, was bei einer bestimmten Art der Ausbildung der Vorsprünge (9) von Vorteil ist.In Fig. 8, a pair of seals (39, 40) is provided regardless of the aforementioned throttling method to the right of the clutch disc in the end position, which is closed when the clutch is in the zero position. It has the purpose of briefly interrupting the flow through the toothing when the torque is reversed (zero crossing), which is advantageous in the case of a specific type of design of the projections (9).

In den Fig. 9 und 10 ist das Primärteil, wie in der Fig. 1, mit (1) bezeichnet, die Bezugszahl (5) bezeichnet das Sekundärteil und (14) die Kupplungsscheibe, welche über Wälzkörper (52) drehfest und axial verschiebbar mit dem Primärteil (1) verbunden ist. Auf der seitlichen Wandung des Sekundärteils (5) und der dieser zugewandten Seite der Kupplungsscheibe (14) sind Kränze von sich axial erstreckenden Vorsprüngen (9) angeordnet, zwischen denen Rollkörper (25) liegen, die im Käfig (27) geführt werden. Die Wälzkörper (52) sind ebenfalls in einem Käfig (53) gehalten, der über Bolzen (54) mit dem äußeren Käfig (27) axial fest und tangential über Längsschlitze (55) relativ verschiebbar verbunden ist.9 and 10, the primary part, as in FIG. 1, is denoted by (1), the reference number (5) denotes the secondary part and (14) the clutch disc, which is rotatably and axially displaceable via rolling elements (52) the primary part (1) is connected. On the side wall of the secondary part (5) and the side of the clutch disc (14) facing it, rings of axially extending projections (9) are arranged, between which there are rolling elements (25) which are guided in the cage (27). The rolling elements (52) are also held in a cage (53) which is axially fixed to the outer cage (27) by means of bolts (54) and is relatively displaceably connected tangentially via longitudinal slots (55).

Bei Einleitung eines Drehmomentes in den Primärteil (1) wird die Kupplungsscheibe (14) durch die Rollkörper (25), die zwischen den Vorsprüngen (9) liegen, mitgenommen und axial verschoben, wobei durch die Axialkomponente Druck auf die Kupplungsscheibe (14) über die Federelemente (8) ausgeübt wird. Die Kupplungsscheibe (14) verschiebt sich unter dem Einfluß der äußeren Kräfte so lange axial, bis sich ein Gleichgewicht zwischen diesen und den Federkräften eingestellt hat. Die Käfige (27 und 53) mit den Rollkörpern (25) und den Wälzkörpern (52) legen dabei die Hälfte des Weges zurück, den die. Kupplungsscheibe (14) ausführt. Der unterschied!iche tangentiale Weg der beiden Käfige wird durch Längsschlitze (55) am Käfig (53) ausgeglichen.When a torque is introduced into the primary part (1), the clutch disc (14) is carried along and axially displaced by the rolling elements (25), which lie between the projections (9), pressure exerted on the clutch disc (14) by the axial component Spring elements (8) is exercised. The clutch disc (14) moves axially under the influence of external forces until an equilibrium has been established between these and the spring forces. The cages (27 and 53) with the rolling elements (25) and the rolling elements (52) cover half the distance that the. Clutch disc (14) executes. The different tangential path of the two cages is compensated for by longitudinal slots (55) on the cage (53).

Claims (24)

1. A torsionally resilient, vibration-damping shaft coupling with liquid damping, the torque transmission of which, from a primary member (1) to a secondary member (5), is effected via a cou--piing member which is disposed between these and which is held against rotation but is axially displaceable by means of projections (9) extending axially and arranged in a ring on a surface perpendicular or substantially perpendicular to the axis of rotation and of recesses having lateral faces inclined towards one another in the circumferential direction in the manner of a crown gear, which coupling member acts on sets of spring elements (8), particularly cup springs, which are arranged axially or coaxially and are supported on the secondary member, characterised in that the spring elements (8) are guided on pins (10) at the inside and that disposed between the clutch disc (14, 20, 21) and the spring elements (8) is a supporting disc (15) which covers all the spring elements radially and which is held against rotation in relation to the pins (10) of the spring elements by means of a pin (16).
2. A shaft coupling according to Claim 1, characterised in that the supporting disc (15) is constructed in the form of a thrust bearing.
3. A shaft coupling according to Claims 1 and 2, characterised in that the supporting disc (15) is provided at the outer circumference and possibly also at the inner circumference, with seals (12,18), and divides the housing into two chambers (31, 32; 41, 42) a throttle opening (30) being provided between the chambers in the vicinity of the axis of rotation.
4. A shaft coupling according to any one of Claims 1 to 3, characterised in that two concentric clutch discs (20, 21) are provided which can be turned in relation to one another and which are provided, at their adjacent sides, with the interengaging projections and recesses (9) arranged in a ring, the one disc (20) being connected at the inside, by teeth (6), to the primary member (1) for rotation therewith but not in relation thereto and for axial displacement, and the other disc (21) being connected at the outside, by teeth (22), to the secondary member (5) for rotation therewith but not in relation thereto and for axial displacement, and sets of spring elements (8) being disposed at both sides of the pair of discs.
5. A shaft coupling according to any one of Claims 1 to 4, characterised in that the projections (9) arranged in a ring are arranged substantially in the middle between the outer and the inner diameters of the clutch discs (14, 20, 21).
6. A shaft coupling according to Claims 1 to 5, characterised in that the lateral faces (9a) of the projections (9) arranged in a ring have an inclination of about 20° to 45°.
7. A shaft coupling according to Claims 1 to 6, characterised in that the inclination of the lateral faces (9a, 9b) of the front and back of the projections (9) is different.
8. A shaft coupling according to Claims 1 to 7, characterised in that the inclination of the lateral faces (9a, 9c) changes during its course, particularly that it becomes greater.
9. A shaft coupling according to any one of Claims 1 to 8, characterised in that rolling bodies (25) are disposed between the lateral faces (9a) of the projections (9).
10. A shaft coupling according to Claim 9, characterised in that the rolling bodies (25) are guided in a cage (27).
11. A shaft coupling according to any one of Claims 1 to 10, characterised in that the clutch discs (14, 20, 21) or the supporting discs (15) are provided with stops (11) to limit the spring excursion.
12. A shaft coupling according to any one of Claims 1 to 11, characterised in that the tension of the spring elements (8) acting axially is adjustable from the outside via adjusting screws.
13. A shaft coupling according to Claim 12, characterised in that the tension of the spring elements (8) is adjusted so that the projections (9) of the clutch discs (14, 20, 21) come out of engagement in the event of excessive torque.
14. A shaft coupling accoupling to any one of Claims 1 to 13, characterised in that the primary member (1) and the secondary member (5) are each provided with an opening (23, 24) for the supply or offtake of damping oil.
15. A shaft coupling according to any one of Claims 1 to 14, characterised in that the primary member (1), in which the driving clutch disc (14, 20) engages, is constructed in the form- of a double-jointed coupling which engages in a hub (19) of the driving or driven machine.
16. A shaft coupling according to Claim 3, characterised in that disposed at the flow passage between the chambers (31, 41, 42) is a tubular control member (33, 46) which is provided with a radial seal (34, 47) at the outer end and which cooperates with corresponding, axially directed channels (37) which are situated in the primary or secondary member (1, 5) and are provided with a plurality of throttle openings (36, 49) which are situated one behind the other in various planes and lead into the interior of the coupling and which are brushed over by the radial seal during the working stroke.
17. A shaft coupling according to Claim 16, characterised in that at least one throttle opening (36, 49) can be varied in its cross-section by means of a regulator (38, 51) from the face of the coupling.
18. A shaft coupling according to Claims 16 and 17, characterised in that the regulator (38, 51) is constructed in the form of a pressure-responsive valve which is adjustable from the outside. 19. A shaft coupling according to Claim 16, characterised in that the radial seal (34, 47) is effective only in parts of the working stroke.
20. A shaft coupling according to Claim 3, characterised in that the coupling teeth (6) serve as a flow passage between the chambers and the control member (33) is disposed on the clutch disc (14).
21. A shaft coupling according to Claim 16, characterised in that bores (44, 45) in the supporting disc (15) and in the adjacent clutch disc (14) are provided as a flow passage between the chambers (42, 41), which bores are situated in the region of the pins (10), while a control member (46) is disposed at each bore (44) of the supporting disc (15).
22. A shaft coupling according to Claim 21, characterised in that disposed on the side of the clutch disc (14) remote from the control member (46) is an axial seal (39) which, in the neutral position of the coupling member, bears against an axial seal (40) disposed on the primary member (1).
23. A shaft coupling according to Claim 10, characterised in that the clutch disc (14) is mounted on the primary member (1) via a rolling-ball connection (52, 53).
24. A shaft coupling according to Claim 23, characterised in that the cage (27) of the rolling bodies is rigidly connected, in the axial direction, via pins (54), to a cage (53) which belongs to the rolling-ball connection and that the relative tangential movement between the cages (27, 53) is compensated by elongated slots (55) in the cage (53).
EP84107975A 1983-07-13 1984-07-07 Rotational flexible coupling with torque variations damping Expired EP0131881B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT84107975T ATE42808T1 (en) 1983-07-13 1984-07-07 TORSIONALLY, VIBRATION-DAMPING SHAFT COUPLING.

Applications Claiming Priority (6)

Application Number Priority Date Filing Date Title
DE19833325214 DE3325214C2 (en) 1983-07-13 1983-07-13 Highly flexible shaft coupling
DE3325214 1983-07-13
DE19843400127 DE3400127A1 (en) 1984-01-04 1984-01-04 Torsionally flexible vibration-damping shaft coupling
DE3400127 1984-01-04
DE19843408286 DE3408286A1 (en) 1984-03-07 1984-03-07 Torsionally elastic vibration damping shaft coupling
DE3408286 1984-03-07

Publications (3)

Publication Number Publication Date
EP0131881A2 EP0131881A2 (en) 1985-01-23
EP0131881A3 EP0131881A3 (en) 1985-10-02
EP0131881B1 true EP0131881B1 (en) 1989-05-03

Family

ID=27191128

Family Applications (1)

Application Number Title Priority Date Filing Date
EP84107975A Expired EP0131881B1 (en) 1983-07-13 1984-07-07 Rotational flexible coupling with torque variations damping

Country Status (5)

Country Link
US (1) US4734080A (en)
EP (1) EP0131881B1 (en)
DE (1) DE3478049D1 (en)
FI (1) FI74118C (en)
NO (1) NO158265C (en)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR101263246B1 (en) 2008-05-30 2013-05-09 오스트리아 오토모티브 시스템즈 아게 torsional vibration damper
EP3997358B1 (en) * 2019-07-12 2024-04-10 Schaeffler Technologies AG & Co. KG Torsional vibration damper

Families Citing this family (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3645264C2 (en) * 1985-06-14 1995-09-28 Gkn Automotive Ag Torsionally flexible, vibration-damping flywheel
DE3831515A1 (en) * 1988-09-16 1990-03-22 Mtu Friedrichshafen Gmbh Torsional vibration damper
US5954552A (en) * 1998-03-13 1999-09-21 Lauterbach; Joachim Combined clutch and torsion damper for water jet propulsion
JP3824048B2 (en) * 2000-09-12 2006-09-20 本田技研工業株式会社 Cam type torque damper mounting structure
DE102004036586A1 (en) * 2004-07-28 2006-03-23 Robert Bosch Gmbh Locking disc and overload clutch with a locking disc
US8113544B2 (en) * 2006-04-07 2012-02-14 Hydril Usa Manufacturing Llc Rotating fluid union
US7926637B2 (en) * 2006-10-16 2011-04-19 Schaeffler Technologies Gmbh & Co. Kg Device for damping vibrations, in particular, torsion vibration damper
WO2010012078A1 (en) * 2008-07-28 2010-02-04 Magna Powertrain Inc. Dual mass flywheel with continuous non-linear system stiffness, overrunning ability, through axial translation against spring system
DE202008012811U1 (en) * 2008-09-26 2010-03-04 Asturia Automotive Systems Ag Hydraulic torsional damper with elastic element
CN101788033B (en) * 2010-02-23 2011-08-31 钱江弹簧(北京)有限公司 Spring combined disk
DE202011002608U1 (en) * 2011-02-11 2012-02-29 Camera Dynamics Gmbh tripod head
DE102014223139A1 (en) * 2014-11-13 2016-05-19 Voith Patent Gmbh torsional vibration damper
DE102015203054B4 (en) * 2015-02-20 2016-09-01 Magna powertrain gmbh & co kg Device for damping torsional vibrations
FR3036153B1 (en) * 2015-05-12 2017-06-09 Messier Bugatti Dowty TRAINING ROLL.
US20180180111A1 (en) * 2016-12-22 2018-06-28 Schaeffler Technologies AG & Co. KG Outer hub wedge clutch
JP7099243B2 (en) 2018-10-17 2022-07-12 スズキ株式会社 Damper device
CN115820292B (en) * 2022-12-09 2024-07-12 扬州东方吊架有限公司 Vertical container damping guide device and annular guide structure

Family Cites Families (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1165381A (en) * 1912-08-13 1915-12-28 Universal Turbine Company Yieldable gearing.
US1126219A (en) * 1913-12-29 1915-01-26 Albert Hupp Shaft-coupling.
US1828370A (en) * 1928-01-19 1931-10-20 Deere & Co Slip clutch
DE740978C (en) * 1938-09-02 1943-11-02 Zahnraederfabrik Augsburg Vorm Safety main coupling for rolling mills
US2333553A (en) * 1941-09-10 1943-11-02 Borg Warner Slip clutch for power take-offs
US2513379A (en) * 1944-09-28 1950-07-04 Dana Corp Friction clutch plate
US2560427A (en) * 1945-09-19 1951-07-10 Kerns Ind Corp Slip cushion coupling
US3166168A (en) * 1961-04-10 1965-01-19 Ingersoll Rand Co Impact tool torsion bar
JPS5038876A (en) * 1973-08-10 1975-04-10
AT332688B (en) * 1973-09-25 1976-10-11 Geislinger Dr Ing Leonard ROTARY VIBRATION DAMPER OR ELASTIC COUPLING
US3942337A (en) * 1974-09-16 1976-03-09 Industrial Analytics Inc. Torque limiting device
SU651151A1 (en) * 1977-09-16 1979-03-05 Предприятие П/Я А-7393 Spring coupling
AT362630B (en) * 1979-10-08 1981-06-10 Geislinger Co Schwingungstechn TURNING VIBRATION DAMPER OR VIBRATION DAMPING AND ELASTIC COUPLING
GB2089000B (en) * 1980-12-08 1985-01-30 Honda Motor Co Ltd Torsional vibration absorber device
DE3228673A1 (en) * 1981-07-31 1983-03-17 Sachs Systemtechnik Gmbh, 8720 Schweinfurt Torsional vibration damper with laterally displaceable damping element

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR101263246B1 (en) 2008-05-30 2013-05-09 오스트리아 오토모티브 시스템즈 아게 torsional vibration damper
EP3997358B1 (en) * 2019-07-12 2024-04-10 Schaeffler Technologies AG & Co. KG Torsional vibration damper

Also Published As

Publication number Publication date
NO158265B (en) 1988-05-02
NO158265C (en) 1988-08-10
NO842788L (en) 1985-01-14
US4734080A (en) 1988-03-29
EP0131881A3 (en) 1985-10-02
EP0131881A2 (en) 1985-01-23
FI74118B (en) 1987-08-31
FI842803A0 (en) 1984-07-11
DE3478049D1 (en) 1989-06-08
FI842803A (en) 1985-01-14
FI74118C (en) 1987-12-10

Similar Documents

Publication Publication Date Title
EP0131881B1 (en) Rotational flexible coupling with torque variations damping
DE102009002481B4 (en) Drive system with torque transmission arrangement and hydrodynamic coupling arrangement
DE19921750B4 (en) transmission
EP0157236B1 (en) Fluid friction coupling, especially for differential gears of motor vehicles
DE10160865B4 (en) Infinitely variable conical-pulley transmission with integrated torque sensor
DE60214995T2 (en) Wet clutch or friction disc brake
DE2848748B2 (en) Elastic coupling in disc design
DE3049645C2 (en)
DE3325214C2 (en) Highly flexible shaft coupling
DE3228673A1 (en) Torsional vibration damper with laterally displaceable damping element
WO2007110026A1 (en) Torque sensing device for a taper disk wraparound drive
DE8122473U1 (en) Torsional vibration damper with laterally displaceable damping element
EP1158207B1 (en) Axial actuator for a variator ,variator and cvt.
EP1729025B1 (en) Mulitple clutch device
DE10304140B3 (en) Friction clutch with adjustment by magneto-rheological fluid
DE3442738A1 (en) Flexible shaft coupling with torsional vibration damping
DE679506C (en) Coupling device for automatically controlled by pressure fluid gear change gear, especially of motor vehicles
DE3821773A1 (en) Coupling device
DE3535339A1 (en) Differential with differential brake
CH648914A5 (en) V-BELT DISC UNIT FOR A V-BELT GEAR WITH VARIABLE TRANSMISSION.
DE4012429A1 (en) Plate spring damping coupling with inner and outer part - has liq. compartments divided into chambers with throttle paths
DE3400127A1 (en) Torsionally flexible vibration-damping shaft coupling
DE4345346C2 (en) Hydraulically damped clutch plate for vehicle
DE3348058C2 (en)
DE2062416A1 (en) Device for the transmission of rotary movements

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Designated state(s): AT BE CH DE FR GB IT LI NL SE

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Designated state(s): AT BE CH DE FR GB IT LI NL SE

17P Request for examination filed

Effective date: 19860327

17Q First examination report despatched

Effective date: 19870123

D17Q First examination report despatched (deleted)
RIN1 Information on inventor provided before grant (corrected)

Inventor name: MASCHINENFABRIK STROMAG GMBH

RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: KROENERT, CURT, DIPL.-ING.

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT BE CH DE FR GB IT LI NL SE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: NL

Effective date: 19890503

Ref country code: BE

Effective date: 19890503

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: SE

Payment date: 19890503

Year of fee payment: 6

REF Corresponds to:

Ref document number: 42808

Country of ref document: AT

Date of ref document: 19890515

Kind code of ref document: T

ITF It: translation for a ep patent filed
REF Corresponds to:

Ref document number: 3478049

Country of ref document: DE

Date of ref document: 19890608

ET Fr: translation filed
PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 19890630

Year of fee payment: 6

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AT

Effective date: 19890707

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 19890714

Year of fee payment: 6

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 19890727

Year of fee payment: 6

ITTA It: last paid annual fee
PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LI

Effective date: 19890731

Ref country code: CH

Effective date: 19890731

GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)
NLV1 Nl: lapsed or annulled due to failure to fulfill the requirements of art. 29p and 29m of the patents act
PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

26N No opposition filed
PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Effective date: 19900707

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Effective date: 19900708

GBPC Gb: european patent ceased through non-payment of renewal fee
PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Effective date: 19910329

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Effective date: 19910403

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

EUG Se: european patent has lapsed

Ref document number: 84107975.9

Effective date: 19910402